US4817460A - Infinitely variable steering transmission - Google Patents

Infinitely variable steering transmission Download PDF

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Publication number
US4817460A
US4817460A US07/128,308 US12830887A US4817460A US 4817460 A US4817460 A US 4817460A US 12830887 A US12830887 A US 12830887A US 4817460 A US4817460 A US 4817460A
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United States
Prior art keywords
output
transmission
gear set
speed
planetary gear
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Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Fee Related
Application number
US07/128,308
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English (en)
Inventor
Bradley O. Reed
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General Dynamics Land Systems Inc
General Electric Co
Original Assignee
General Electric Co
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Publication date
Application filed by General Electric Co filed Critical General Electric Co
Assigned to GENERAL ELECTRIC COMPANY, A NY CORP reassignment GENERAL ELECTRIC COMPANY, A NY CORP ASSIGNMENT OF ASSIGNORS INTEREST. Assignors: REED, BRADLEY O.
Priority to US07/128,308 priority Critical patent/US4817460A/en
Priority to AU25094/88A priority patent/AU604445B2/en
Priority to IL88401A priority patent/IL88401A/xx
Priority to EP19880311457 priority patent/EP0319323A3/de
Priority to JP63304262A priority patent/JPH01208267A/ja
Priority to KR1019880016052A priority patent/KR890009709A/ko
Publication of US4817460A publication Critical patent/US4817460A/en
Application granted granted Critical
Assigned to GENERAL DYNAMICS DEFENSE SYSTEMS, INC. reassignment GENERAL DYNAMICS DEFENSE SYSTEMS, INC. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: LOCKHEED MARTIN CORPORATION
Assigned to GENERAL DYNAMICS LAND SYSTEMS, INC. reassignment GENERAL DYNAMICS LAND SYSTEMS, INC. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: GENERAL DYNAMICS DEFENSE SYSTEMS, INC.
Anticipated expiration legal-status Critical
Expired - Fee Related legal-status Critical Current

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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
    • B62D—MOTOR VEHICLES; TRAILERS
    • B62D3/00—Steering gears
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
    • B62D—MOTOR VEHICLES; TRAILERS
    • B62D11/00—Steering non-deflectable wheels; Steering endless tracks or the like
    • B62D11/02—Steering non-deflectable wheels; Steering endless tracks or the like by differentially driving ground-engaging elements on opposite vehicle sides
    • B62D11/06—Steering non-deflectable wheels; Steering endless tracks or the like by differentially driving ground-engaging elements on opposite vehicle sides by means of a single main power source
    • B62D11/10—Steering non-deflectable wheels; Steering endless tracks or the like by differentially driving ground-engaging elements on opposite vehicle sides by means of a single main power source using gearings with differential power outputs on opposite sides, e.g. twin-differential or epicyclic gears
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/19—Gearing
    • Y10T74/19023—Plural power paths to and/or from gearing
    • Y10T74/19037—One path includes fluid drive

Definitions

  • the present invention relates to multi-range steering transmissions for track-laying or skid-steered, wheeled vehicles.
  • An exemplary steering transmission of this type typically utilizes at least one and in most instances two separate hydraulic drive units mechanically driven by a prime mover at a normally constant speed and capable of developing, within limits, infinitely variable speed, bidirectional, hydrostatic outputs for ultimate application to the left and right transmission output shafts.
  • These hydrostatic outputs are typically utilized alone to hydrostatically drive the transmission output shafts in a forward and reverse first propulsion range and are combined with mechanical inputs from the prime mover to hydromechanically drive the transmission output shafts in at least one and typically several higher forward propulsion ranges.
  • Changes in the hydrostatic output speed provide infinite speed variation within the various ranges and ideally can also be utilized to effect steering by differentially varying the speeds of the two hydrostatic outputs.
  • a typical hydraulic drive unit may be of the type disclosed in Applicant's U.S. Pat. No. 3,815,698 entitled "Hydromechanical Steering Transmission” and, as such, includes a variable capacity ball piston pump and a normally fixed capacity ball piston motor connected in hydraulic fluid-coupled relation.
  • the pumps are driven at a constant speed by the prime mover, and the motors develop the hydrostatic outputs.
  • the pump capacities i.e., "stroking” as it is known in the art
  • the speeds of the motor hydrostatic outputs are varied accordingly.
  • the eccentricity of the pumps the rotational direction of the motor hydrostatic outputs are reversed.
  • An additional object is to provide an infinitely variable steering transmission of the above-character, wherein the infinitely variable speed capability is provided in a simplified and efficient manner.
  • a further object is to provide an infinitely variable steering transmission of the above-character which is inexpensive to manufacture, requires a relatively low number of component parts, and is compact and light in weight, and is efficient in operation.
  • an infinitely variable steering transmission for track-laying vehicles which utilizes drive units of the type which are capable of developing, in response to a constant speed mechanical input, an output speed infinitely variable between a minimum speed less than input speed and a maximum speed greater than input speed.
  • drive units can not however provide neutral (zero output speed) and their outputs are unidirectional (non-reversing).
  • variable speed outputs of the two drive units are respectively applied to left and right output planetary gear sets drivingly connected with the left and right transmission output shafts.
  • the constant speed mechanical input of the prime mover is applied via an input planetary gear set to both output planetary gear sets for interaction with the drive unit outputs to drive the transmission output shafts through either a forward and reverse first propulsion range or a forward third propulsion range depending upon the reaction to the prime mover constant speed mechanical input selectively established in the input planetary gear set.
  • This constant speed mechanical input also fixes the speeds of corresponding gear elements of both output planetary gear sets during first and third range steering maneuvers effected by increasing the output speed of one drive unit by the same increment that the output speed of the other drive unit is decreased.
  • the input planetary gear set is inactivated, and thus the transmission output shafts are driven exclusively by the drive unit outputs.
  • the outputs of both drive units are combined by one of the output planetary gear sets to produce a steer cancelling effect in both output planetary gear sets, to establish the same steering convention as exists in the first and third ranges, and to accommodate a speed stroking control pattern for the drive units which is devoid of discontinuities as the vehicle is accelerated through the forward propulsion ranges.
  • FIG. 1 is a schematic illustration of an infinitely variable steering transmission constructed in accordance with the present invention
  • FIG. 2 is a graph illustrating the operations of the two output planetary gear sets in the steering transmission of FIG. 1;
  • FIG. 3 is a graph of drive unit speed (RPM) versus vehicle speed (MPH) to illustrate the stroking pattern for the drive units in the transmission of FIG. 1 to achieve acceleration through the plural speed ranges.
  • RPM drive unit speed
  • MPH vehicle speed
  • the track laying vehicle steering transmission of the present invention includes a first drive unit 12 and a second, identical drive unit 14.
  • These drive units are, in accordance with the present invention, a type of transmission unit that provides in response to a constant speed input drive, an infinitely variable speed output ranging from some minimum speed less than input speed to some maximum speed greater than input speed.
  • Other characteristics of this type of drive unit are that its direction of output drive cannot be reversed, i.e., no reverse capability, and its output speed does not go to zero, i.e., no neutral.
  • Such drive units may take a variety of forms, such as toroidal traction drive units, V-belt drives having variable diameter pulleys, and the like.
  • the identical, input drives to drive units 12 and 14, indicated at 13 and 15, respectively, are obtained from a suitable vehicle prime mover 8, such as a diesel or gas turbine engine operating at constant speed.
  • the variable speed output of drive unit 12 appears on output shaft 16 on which is mounted a pinion gear 18 which drives a spur gear 22 carried by a sleeve shaft 24.
  • the sun gear 26s of a right output planetary gear set are also carried by this sleeve shaft.
  • the same constant speed input drive that is applied to drive units 12 and 14 is also applied, as indicated at 27, to a spur gear 28 mounted on a sleeve shaft 30 which also carries the sun gear 32s of an input planetary gear set, generally indicated at 32.
  • Planetary pinion gears 32p of input planetary gear set 32 and planetary pinion gears 26p of output planetary gear set 26 are mounted on a common carrier, indicated at 34. Ring gear 26r of the output planetary gear set is directly connected to the right transmission output shaft 36. Ring gear 32r of input planetary gear set 32 is grounded upon activation of a brake BI(R) to put transmission 10 in a forward/reverse first speed range.
  • Output shaft 40 of drive unit 14 carries a pinion gear 42 which meshes with a spur gear 44 carried on a sleeve shaft 46.
  • the ratio between gears 42 and 44 is the same as the ratio between gears 18 and 22.
  • Sleeve shaft 46 also mounts the sun gear 48s of a left output planetary gear set, generally indicated at 48.
  • Pinion gears 48p are mounted on a planetary carrier 48c which is physically connected via a cross shaft 50 to the common carrier 34 of planetary gear sets 32 and 26.
  • Ring gear 48r of the left output planetary gear set 48 is directly connected with the left transmission output shaft 52.
  • Brakes B1 and B2 are activated to ground ring gears 48r and 26r, respectively, and thus serve as vehicle stopping and parking brakes.
  • output shaft 16 of drive unit 12 Upon engagement of a clutch CII, output shaft 16 of drive unit 12 also drives a pinion gear 54 which, in turn, drives a spur gear 58 directly connected to ring gear 48r of left output planetary gear set 48.
  • clutch CII is engaged to apply the variable speed output of drive unit 12 to ring gear 48r of left output planetary gear set 48 and thence to left transmission output shaft 52 when transmission 10 is shifted into a second forward propulsion speed range.
  • brake BI(R) is engaged to ground ring gear 32r of input planetary gear set 32. Since the constant speed prime mover input is driving sun gear 32s of input planetary gear set 32, common carrier 34 is driven at a reduced constant speed determined by the sun to carrier reduction of this planetary gear set. By virtue of the interconnecting cross shaft 50, planetary carrier 48c of left output planetary gear set 48 is driven at the same fixed reduced speed as common planetary carrier 34.
  • variable speed output of drive unit 12 is being applied as a separate mechanical input to sun gear 26s
  • variable speed output drive of drive unit 14 is being applied as yet another separate mechanical input to sun gear 48s.
  • the two output ring gears 26r and 48r and thus transmission output shafts 36 and 52 are driven into rotation at speeds which are functions of the two mechanical inputs applied to each of the two output planetary gear sets.
  • FIG. 2 is a graphical illustration of the relative angular velocities of the various elements of the two output planetary gear sets.
  • vertical line 60 represents the velocity operating range of sun gear 48s
  • vertical line 61 represents the velocity operating range of carrier 48c
  • vertical line 62 represents the velocity operating range of ring gear 48r.
  • vertical lines 63, 64 and 65 represent the velocity operating range of sun gear 26s, carrier 34, and ring gear 26r, respectively.
  • the horizontal separation of vertical lines 60 and 61 is proportional to the number of teeth on ring gear 48r, while the horizontal separation of vertical lines 61 and 62 is proportional to the number of teeth on sun gear 48s.
  • the horizontal separation between vertical lines 60 and 62 is proportional to the sum of the ring gear 48r and sun gear 48s teeth.
  • the same proportionalities apply for the horizontal separations between vertical lines 63-65 for output planetary gear set 26. Since the two output planetary gear sets are of identical gears ratios, the separations between corresponding vertical lines are identical in each case.
  • X axis 66 represents zero revolutions per minute (RPM), and points on vertical operating lines 60-65 correspond to the angular velocities of the respective planetary gear elements represented by these lines.
  • Points above this axis 66 represent angular velocities in the forward propulsion direction, while points below this axis represent angular velocities in the reverse propulsion direction.
  • a characteristic of planetary gears such as planetary gear 26 and 48 is that, under all operating conditions, the velocity points on the vertical operating lines of the various planetary gear elements will always lie on a single straight line. Thus, when two of the velocity operating points of the three planetary gear elements are known, the third velocity point will always lie on a straight line drawn through the two known velocity points.
  • drive units 12 and 14 are capable of producing output speeds varying from a predetermined reduction relative to constant input speeds to a predetermined overdrive relative to constant input speed. It will be assumed that these drive units are capable of providing infinitely variable output speeds ranging from a two to one reduction relative to input speed to a one to two step up or overdrive relative to input speed.
  • velocity points 67, 68 and 69 on sun gear 48s vertical operating line 60 represent drive unit speed ratios of two to one, one to one and one to two, respectively.
  • Velocity point 70 represents the mid point speed of this velocity spectrum, which is 1 to 1.25.
  • Corresponding velocity points 67-70 are also shown on sun gear 26s vertical operating line 63.
  • the gear ratio of input planetary gear set 32 and the identical gear ratios for the two output planetary gear sets 26, 48 are established such that when sun gear 26s is driven by drive unit 12 at an angular velocity which corresponds to the midpoint of its velocity spectrum, i.e., velocity point 70 on line 63, the angular velocity of ring gear 26r is zero.
  • This operating condition is satisfied if common carrier 34 is made to rotate by the prime mover acting through planetary gear set 32 at a velocity corresponding to point 71. Under these conditions, a straight line 72 drawn through points 70 and 71 intersects ring gear 26r operating line 65 at point 72 which lies on zero velocity axis 66. Since planetary carrier 34 is rigidly connected to planetary carrier 48c by cross shaft 50 (FIG.
  • the preferred convention for executing a steer is to increase the output speed of one drive unit 12, 14 by a predetermined amount, while decreasing the output speed of the other drive unit by the same predetermined amount. This has the effect of proportionately increasing the output speed of one transmission output shaft 36, 52 while decreasing the output speed of the other transmission output shaft by an equal amount. It can readily be seen from FIG. 2 that if the angular velocity of sun gear 26s is increased a given amount by increasing the output speed of drive unit 12, and the angular velocity of sun gear 48s is decreased by the same amount by decreasing the output speed of drive unit 14, the angular velocities of ring gears 26r and 48r respectively decrease and increase by equal amounts to effect a steer to the right.
  • a steer to the left is executed.
  • the execution of a steer simply results in the straight operating line for planetary gear set 26 being rocked about the fixed velocity point of its carrier 34 in one direction, while the straight operating line for planetary gear set 48 is rocked through an equal arc in the opposite direction about the fixed velocity point of its carrier 48c; these carrier velocity points thus serving as fulcrums.
  • the degree of steer may be varied by increasing or decreasing the magnitudes of the increments by which the output speeds of the drive units are increased on the one hand and decreased on the other.
  • third forward propulsion range operation Before describing the operation of transmission 10 in its second forward propulsion range, third forward propulsion range operation will be described because it is basically identical to first forward propulsion range operation.
  • brake BI(R) is released.
  • third range clutch CIII is engaged. This is seen to apply the constant speed input of prime mover 8 on sleeve shaft 30 directly to common planetary carrier 34 and also to planetary carrier 48c via cross shaft 50. In FIG. 2 this is seen to impose an angular velocity on these carriers which is represented by velocity points 80 on carrier vertical operating lines 61 and 64 which are horizontally aligned with points 68 on sun gear 48s vertical operating line 60 and sun gear 26s vertical operating line 63.
  • velocity points 68 correspond to a one to one speed ratio being established in drive units 12 and 14, and thus their output speeds are both equal to the speed of the prime mover mechanical input. It is seen that speed variations in the third propulsion range are effected in exactly the same manner as in the first propulsion range.
  • Drive units 12 and 14 are uniformly stroked downwardly in speed from points 69 on the sun gear vertical operating lines to velocity points 67 in order to speed up through the third propulsion range. This is confirmed in FIG. 2 as straight lines 81 drawn for the two output planetary sets from points 69 through points 80 intersect the ring gear vertical operating lines at points 82, which represent minimum speed in the third propulsion range.
  • third forward propulsion speed range can be represented by the double pointed arrows 85 in FIG. 2.
  • Third range steer is effected simply by respectively increasing and decreasing the output speeds of drive limits 12 and 14 by equal amounts, which has the effect of rocking operating lines of the left and right output planetary gear sets through equal angles in opposite directions about the fixed velocity point fulcrums 80 imposed on carriers 48c and 34 by the constant speed prime mover input.
  • brake BI(R) is released, and second range clutch CII is engaged.
  • FIG. 1 This is seen in FIG. 1 to create the condition wherein the variable speed output of drive unit 12 is applied not only to sun gear 26s of right output planetary gear set 26, but also to ring gear 48r of left output planetary gear set 48 via pinion gear 54 and spur gear 58.
  • left output planetary gear set 48 receives two mechanical inputs, the first being the variable speed output of drive unit 14 on its sun gear 48s and the second being the variable speed output of drive unit 12 on its ring gear 48r.
  • brake BI(R) since brake BI(R) is released, there is no reaction force in input planetary gear set 32 to the prime mover input on sun gear 32s, and thus this constant speed input does not drive common carrier 34 during second range forward propulsion.
  • the straight operating line 88 for right output planetary gear 26 drawn through points 70 and 89 intersects the ring gear 26r vertical operating line 65 at point 87 whose vertical position is the same as that of velocity point 87 on ring gear 48r vertical operating line 62.
  • the second forward propulsion range fills in the gap between the first and third forward propulsion ranges, with second range limits represented by double pointed arrows 95.
  • This graphical demonstration that the speed imposed on ring gear 48r and thus left output shaft 52 by drive unit 12 is duplicated on right output shaft 36, can also be readily seen in FIG. 1 since, during straight ahead second range propulsion, the sun gears and carriers of the two identical planetary gear sets are respectively moving at the same angular velocities, and therefore their ring gears are constrained to move at the same angular velocity as well.
  • the drive units are stroked downwardly, as represented by straight line section 90a through first range propulsion in the reverse and then forward directions, stroked upwardly, as represented by straight line segment 90b, for forward propulsion through the second range, and then stroked downwardly, as represented by straight line segment 90c, for forward propulsion in the third range.
  • This drive unit stroking pattern is continuous from range to range, and thus range shifting does not require abrupt changes in drive unit speed.
  • second range steer It is obviously extremely important that the steering convention as described above with respect to the first and third ranges be the same for the second range. That is, operator control and vehicle response during its steer should not vary from range to range.
  • steering in all three range must be effected by the same equal and opposite strokings of the two drive units 12 and 14. That is, a steer to the right must be effected by increasing the output speed of drive unit 12 by a preselected amount accompanied by decreasing the output speed of drive unit 14 by the same amount, and vice versa.
  • the mechanical speed inputs to the left output planetary gear set must be such that as the angular velocities of ring gear 48r and sun gear 48s are varied in relatively opposite directions, an average of these two speed inputs must be developed on carrier 48c. That is, an increase in the angular velocity of sun gear 48s which would tend to increase the angular velocity of carrier 48c must be exactly offset by an appropriate decrease in the angular velocity of ring gear 48r.
  • second range clutch CII becomes synchronous, i.e., output shaft 16 of drive unit 12 is rotating at the same angular velocity as pinion 54 is being rotated by ring gear 48r via spur gear 58. This represents an opportune time to shift from the first forward propulsion range into the second forward propulsion range by engaging clutch CII and releasing brake BI(R).
  • third range clutch CIII becomes synchronous in that carrier 34 is revolving at the same angular velocity as sleeve shaft 30. At this time, shifting from the second forward propulsion range into the third propulsion range can be smoothly effected by engaging the third range clutch CIII as clutch CII is disengaged.
  • first second and third range forward propulsion limits represented in FIG. 3 by arrows 78, 95 and 85, respectively, are not in practice end-to-end as illustrated.
  • At least twenty percent of the first range extends at its upper end into the lower end of the second speed range, and at least twenty percent of the second speed range extends at its upper end into the lower end of the third speed range to accommodate the synchronous range shifting described above.
  • This speed overlap is also desirable to have available additional speed variation in the drive units 12, 14 for steering while the transmission is being operated near its range shifting points.
  • the present invention provides a multi-range, infinitely variable, integral steering transmission for tracklaying vehicles, which is compact in size and inexpensive to manufacture, requires a minimal number of component parts, is efficient in operation and affords positive and uniform operator control in all of its multiple speed ranges. It is therefore seen that the objects set forth above, including those made apparent from the preceding description are efficiently attained, and, since certain changes may be made in the disclosed embodiment without departing from the scope of the invention, it is intended that all matter contained in the above description and shown in the accompanying drawings be interpreted as illustrated and not in a limiting sense.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Transportation (AREA)
  • Mechanical Engineering (AREA)
  • Structure Of Transmissions (AREA)
  • Non-Deflectable Wheels, Steering Of Trailers, Or Other Steering (AREA)
US07/128,308 1987-12-03 1987-12-03 Infinitely variable steering transmission Expired - Fee Related US4817460A (en)

Priority Applications (6)

Application Number Priority Date Filing Date Title
US07/128,308 US4817460A (en) 1987-12-03 1987-12-03 Infinitely variable steering transmission
AU25094/88A AU604445B2 (en) 1987-12-03 1988-11-11 Infinitely variable steering transmission
IL88401A IL88401A (en) 1987-12-03 1988-11-17 Infinitely variable steering transmission
JP63304262A JPH01208267A (ja) 1987-12-03 1988-12-02 舵取伝動装置
EP19880311457 EP0319323A3 (de) 1987-12-03 1988-12-02 Stufenlos verstellbares Lenkgetriebe
KR1019880016052A KR890009709A (ko) 1987-12-03 1988-12-02 무한 변속 조향 전동 장치

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US07/128,308 US4817460A (en) 1987-12-03 1987-12-03 Infinitely variable steering transmission

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US4817460A true US4817460A (en) 1989-04-04

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US07/128,308 Expired - Fee Related US4817460A (en) 1987-12-03 1987-12-03 Infinitely variable steering transmission

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US (1) US4817460A (de)
EP (1) EP0319323A3 (de)
JP (1) JPH01208267A (de)
KR (1) KR890009709A (de)
AU (1) AU604445B2 (de)
IL (1) IL88401A (de)

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5168946A (en) * 1991-09-09 1992-12-08 General Electric Company Track-laying vehicle electric drive system
US5509491A (en) * 1994-04-18 1996-04-23 General Motors Corporation Dual-motor electric drive system for vehicles
US5730678A (en) * 1996-02-28 1998-03-24 Gen Dynamics Defense Syst Inc Multi-range, hydromechanical transmission for motor vehicles
US6105704A (en) * 1995-09-11 2000-08-22 Honda Giken Kogyo Kabushiki Kaisha Coupling device between left and right wheels of vehicle
US20040098988A1 (en) * 2001-02-08 2004-05-27 Tatsuhiko Goi Uniaxial gas turbine system
US6783474B2 (en) 2001-12-28 2004-08-31 Visteon Global Technologies, Inc. Torque controller for controlling torque to two or more shafts
US20040211615A1 (en) * 2001-10-17 2004-10-28 Oxley Lonnie R. Variable flow control devices, related applications, and related methods
US20060205553A1 (en) * 2002-02-11 2006-09-14 Lee Paul Z Continuously variable ratio transmission
US7108096B1 (en) 2002-02-25 2006-09-19 Lonmore, Lc Vehicle control system with slow-in-turn capabilities and related method
US20220003170A1 (en) * 2018-11-19 2022-01-06 Kawasaki Jukogyo Kabushiki Kaisha Electric power generation controller for use in aircraft

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Publication number Priority date Publication date Assignee Title
DE19631014C2 (de) * 1996-08-01 2003-05-28 Zahnradfabrik Friedrichshafen Hydrostatisch-mechanisches Lenkgetriebe
DE19631012C2 (de) * 1996-08-01 2003-12-11 Zahnradfabrik Friedrichshafen Vorrichtung zur Lenkung eines Kettenfahrzeuges und Verfahren zum Betrieb dieser Vorrichtung
DE10344711A1 (de) 2003-09-26 2005-04-14 Zf Friedrichshafen Ag Elektrisches Antriebssystem für ein Fahrzeug mit Rutschlenkung
DE102005010516A1 (de) * 2005-03-08 2006-09-21 Zf Friedrichshafen Ag Elektrisches Antriebssystem für den Antrieb der beiden Räder eines Antriebsräderpaares

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US3545303A (en) * 1968-09-27 1970-12-08 Avco Corp Steering apparatus for transmissions coupled to a free power turbine
US3575066A (en) * 1969-09-23 1971-04-13 Gen Motors Corp Transmission
US3583256A (en) * 1969-11-19 1971-06-08 Gen Motors Corp Transmission
US3590658A (en) * 1967-09-28 1971-07-06 Robert M Tuck Power train
US4345488A (en) * 1980-04-21 1982-08-24 General Electric Company Hydromechanical steering transmission
DE3305295A1 (de) * 1982-02-17 1983-08-25 Kabushiki Kaisha Komatsu Seisakusho, Tokyo Umschaltvorrichtung zum automatischen wechsel des geschwindigkeitsbereichs in hydromechanischen getrieben
US4485691A (en) * 1982-08-26 1984-12-04 General Electric Company Simplified hydromechanical steering transmission
JPS60227045A (ja) * 1984-04-25 1985-11-12 Mitsubishi Heavy Ind Ltd 変速操向装置
US4569251A (en) * 1983-08-25 1986-02-11 Leyland Vehicles Limited Driveline for a track-laying vehicle with continuously variable steering and propulsion transmissions
US4682515A (en) * 1984-10-11 1987-07-28 General Electric Company Gear train for four range hydromechanical steering transmission
US4718299A (en) * 1984-02-07 1988-01-12 Leyland Vehicles Limited Driveline for a track laying vehicle

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US3815698A (en) * 1972-04-20 1974-06-11 Gen Electric Hydromechanical steering transmission
DE3709191A1 (de) * 1986-04-10 1988-05-11 Michael Meyerle Stufenloses verzweigungsgetriebe insbesondere fuer kraftfahrzeuge

Patent Citations (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3590658A (en) * 1967-09-28 1971-07-06 Robert M Tuck Power train
US3545303A (en) * 1968-09-27 1970-12-08 Avco Corp Steering apparatus for transmissions coupled to a free power turbine
US3575066A (en) * 1969-09-23 1971-04-13 Gen Motors Corp Transmission
US3583256A (en) * 1969-11-19 1971-06-08 Gen Motors Corp Transmission
US4345488A (en) * 1980-04-21 1982-08-24 General Electric Company Hydromechanical steering transmission
DE3305295A1 (de) * 1982-02-17 1983-08-25 Kabushiki Kaisha Komatsu Seisakusho, Tokyo Umschaltvorrichtung zum automatischen wechsel des geschwindigkeitsbereichs in hydromechanischen getrieben
US4485691A (en) * 1982-08-26 1984-12-04 General Electric Company Simplified hydromechanical steering transmission
US4569251A (en) * 1983-08-25 1986-02-11 Leyland Vehicles Limited Driveline for a track-laying vehicle with continuously variable steering and propulsion transmissions
US4718299A (en) * 1984-02-07 1988-01-12 Leyland Vehicles Limited Driveline for a track laying vehicle
JPS60227045A (ja) * 1984-04-25 1985-11-12 Mitsubishi Heavy Ind Ltd 変速操向装置
US4682515A (en) * 1984-10-11 1987-07-28 General Electric Company Gear train for four range hydromechanical steering transmission

Cited By (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5168946A (en) * 1991-09-09 1992-12-08 General Electric Company Track-laying vehicle electric drive system
US5509491A (en) * 1994-04-18 1996-04-23 General Motors Corporation Dual-motor electric drive system for vehicles
US6105704A (en) * 1995-09-11 2000-08-22 Honda Giken Kogyo Kabushiki Kaisha Coupling device between left and right wheels of vehicle
US6325736B1 (en) 1995-09-11 2001-12-04 Honda Giken Kogyo Kabushiki Kaisha Coupling device between left and right wheels of vehicle
US5730678A (en) * 1996-02-28 1998-03-24 Gen Dynamics Defense Syst Inc Multi-range, hydromechanical transmission for motor vehicles
US20040098988A1 (en) * 2001-02-08 2004-05-27 Tatsuhiko Goi Uniaxial gas turbine system
US7028461B2 (en) * 2001-02-08 2006-04-18 Kawasaki Jukogyo Kabushiki Kaisha Uniaxial gas turbine system
US7216579B2 (en) 2001-10-17 2007-05-15 Lonmore, L.C. Variable flow control devices, related applications, and related methods
US20040211615A1 (en) * 2001-10-17 2004-10-28 Oxley Lonnie R. Variable flow control devices, related applications, and related methods
US6783474B2 (en) 2001-12-28 2004-08-31 Visteon Global Technologies, Inc. Torque controller for controlling torque to two or more shafts
US20060205553A1 (en) * 2002-02-11 2006-09-14 Lee Paul Z Continuously variable ratio transmission
US7108096B1 (en) 2002-02-25 2006-09-19 Lonmore, Lc Vehicle control system with slow-in-turn capabilities and related method
US20220003170A1 (en) * 2018-11-19 2022-01-06 Kawasaki Jukogyo Kabushiki Kaisha Electric power generation controller for use in aircraft
US11834999B2 (en) * 2018-11-19 2023-12-05 Kawasaki Jukogyo Kabushiki Kaisha Electric power generation controller for use in aircraft

Also Published As

Publication number Publication date
KR890009709A (ko) 1989-08-03
EP0319323A2 (de) 1989-06-07
AU2509488A (en) 1989-06-08
IL88401A (en) 1991-04-15
EP0319323A3 (de) 1990-09-05
IL88401A0 (en) 1989-06-30
AU604445B2 (en) 1990-12-13
JPH01208267A (ja) 1989-08-22

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